Friction clutch



Jan; 7, 1941. R, A, CARLSON 2,413,810

FRICTION CLUTCH Orgingl Filed Feb. 14, 1941 2 Sheets-Shoot 1 .9 fz.' .2JIJ\ 347 y as J7 m4 A? 2'5"' da J2 J. j 7l j" .um Jaaa e jf d, 27

,eg JJ fff J Jl Jan. 7, 1947. R. A, CARLSON 2,413,810

FRICTION CLUTQH Original Filed Feb. 14, 1941 l 2 Sheets-Skeet 2 fnvenzrfF 727.0720.f Q' af-Zaan -FZM/f /JQ l l Patented Jan. 7, 1947 FBICTIONCLUTCH `Raymond A. Carlson, Rockford, lll., asslgnor to Borg-WarnerCorporation, Chicago, Ill., a corporation of Illinois Originalapplication February 14, 1941, Serial No.

Divided and this application October 9,1943, serial No. 505,604

(cl. 19a-6s) 6 Claims. 1

This invention relates to friction clutches and particularly to animproved arrangement of driving and engaging means for the frictionfacing assembly.

.This is a division of my United States application, Serial No. 378,848.led February 14, 1941, which issued as Patent No. 2,334,382.

It is an object of the invention to provide, in

a friction clutch of the typevwherein the facing carrying means is inthe form of an annulus having driving connection with an encirclingdrive transmitting member and having peripheral teeth meshing withinternal teeth on said drive transmitting member, meansfor minimizingbacklash between saidteeth., To this end, the invention contemplates theformation of the facing supporting annulus in the form of a plurality ofcircumferentially separated segments to which the facings are secured,and the provision of additional segments which are loosely received inthe spaces defined between said facings and the ends of the othersegments and are provided with peripheral teeth adapted to snugly engagethe teeth of the drive transmitting member under the effect ofcentrifugal force.. Thus the loose additional segments, when grippedbetween the friction facings prevent independent movement of the facingsupporting segments which would create backlash between said lattersegments and the drive transmitting member.

Other objects, the advantages and uses of the invention will become moreapparent after reading the following specification and claims, and afterconsideration of the drawings forming a part of the specification,wherein:

Fig. l is an axialv sectional view of a clutch embodying my invention,the clutch being shown in engaged relation;

Fig. 2 is an axial sectional view showing 'the clutch disengaged; and

Fig. 3 is a transverse sectional view of the clutch, taken on the line3--3 of Fig. 1.

As an example oi one form in which the in vention may be embodied, Ihave shown in the drawings a clutch of the heavy duty industrial type,including a drive transmitting member Il) having openings II by means ofwhich it may be attached to a driving member such as for example, aywheel, and having internal teeth I2 for transmitting drive to a drivingclutch element indicated generally at I3. The driving element pressureof clutch engagement.

I3 includes a plurality of circumferentially sepa- 2 rial. Interposedbetween the segments I4 are a plurality of 4loose segments I1 ofsubstantially the same thickness as the segments I4 so as to cooperatewith the segments I4 in maintaining the facings I6 in parallel planeswhile taking the The segments I1 are confined between the facings I6,the segments I4, and the drive ring II.

The segments I4 and I1 are provided with peripheral teeth 9 and 9arespectively meshing with the internal teeth I2roi the drive ring I0.The teeth on the loose segments I 1 are adapted to snugly engage theteeth I2 under the effect of centrifugal force, so as to take up thebacklash between the facings and the drive ring I0, as will later bepointed out.

The facings I6 are adapted to be engaged between a pair of drivenelements I9 and 20, the

element I9 having a hub portion 2| which is.

splined upon a driven shaft 22 and the element 20 having internal teeth23 meshing with splines 24 on the hu-b' portion 2l so as to be drivinglyconnected thereto while capable of axial shifting movement to permitclutch engagement.

Mounted on the shaft 22 for axial shifting movement is a sleeve 25 whichis connected through the medium of an end thrust bearing 26 with acollar 21 having trunnions 28 adapted to coact with a shifting fork ofconventional design. Secured upon thesleeve 25 is an operating cam ring29 having a frusto-conical cam surface 30 terminating in a reentrantlocking groove 3i.

Linkage for transmitting clutch operating movement from the cam 29 tothe driven clutching elements I9 and 20, includes a pluralityof levers32 each fulcrumed on a pivot pin 33 mounted between a pair of ears 340ia fulcrum member 35 which is flxedly associated with the driven elementI9 andshaft 22 as for example, by means of thel machine screws 1securing it to the driven element I9. The levers 32 are in the form ofbell cranks, each including an arm 36 extending in a generally axialdirection and an ann 31 exr tending radially inwardly. The arm 3S isformed A at its end with a fork 38 in which is journalleda roller 39adapted to coact with thecam face 30.

The transmitting linkage further manual adjustment mean-s, indicatedgenerally at 8, and resilient transmission links, indicated generally atI8, both interposed in series with each other between the levers 32 andthe driven element 20.

The adjustment means 8 comprises an adjusting cam ring 44 rand aplurality of levers 40, the ring 44 being carried by the driven element28 includes and the levers 40 being operatively interposed between thering 44 and the resilient link I8. The levers 40 are embraced betweenthe ears 34 of the fulcrum member and are fulcrumed on pivot pins 4Imounted inthe ears 34 outwardly of the levers 32. The inner arms of theleversv 40 are bifurcated to provide spaced furcations 53 which embracethe levers 32. The outer arms 42 of the levers 40 are engaged againstcam surfaces 43 on the adjusting ring 44. The ring 44 has a flange 45which is secured against the rear face of the driven element 20 by meansof screws 48. The screws 48 extend through openings 41 in the flange 45and may be removed to permit the ring 44 to be rotated with reference tothe driven element 2li and reinserted through different openings 41.

The resilient links I8 are mounted in axially extending cylindricalbores 48 in the hub portion4 2| of the driven element I9. Each link I8includes a coil spring 49, a draw bolt 50 and a washer I, the -spring 49being engagedbetween the washer 5I and a head 52 on one end of the drawbolt 50. The head 52 and washer 5I are fitted loosely in the bore 48 soas to be axially slidable therein. s

The resilient links are each operatively interposed between an arm 31 ofa lever 32 and the furcations 53 of the corresponding lever 40. y Thearm 31 has at its end a fork embracing the bolt 50, received in notches54 formed in thesides of the bolt, and acting against a head 55 deningone extremity of thel respective notches 54. The furcations 53 of thelever 40 are engaged against arcuate end surfaces 56 of a pair of wings51 formed on the washer 5I.

Rotation of the adjustment ring 44 with reference to the driven element20 causes the levers 49 to be adjusted in a clockwise direction aroundtheir pivots 4I, the furcations 53 moving to the left and compressingthe springs 49.

The cam ring 44 forms a support for a clutch I cover B0 which has a ring6I snugly fitted on the periphery of the cam ring 44 and tapersrearwardly and inwardly to an opening 32 which receives the operatingmember 2|.

In the operation of the clutch, assuming it to 4 load. When the clutchbegins to rotate, the loose additional segments I1 are centrifugallymoved outward so that their teeth 9a fit snugly into internal teeth I2on the drive transmitting ring I0. When pressure members I9 and 20 havemoved into frictional engagement with the facings I6 as above described,the clutch is fully coupled and the fixed as well as the loose segmentsI4 and I1 are firmly held between the facings. Due to the snug flt ofteeth 9a with ring teeth I2 there can be no relative rotative movementbetween' any of the clamped parts, including the ring teeth I2 and thefixed segment teeth 9, and consequently backlash between these lattermeshed teeth is impossible.

The cam surface 30 of the operating member provides for considerablymore movement of the levers 32 than is necessary for advancing thedriven elements into engagement with the drive element. The surplusmovement is'absorbed in the compression of the spring 49. This surplusmovement is utilized to take up slack -in the linkage that wouldotherwise be occasioned by wearing down of the facings. Thus theyielding transmission links vI8 provide for automatic adjustment forfacing wear within a limited range.

When this range of adjustment has been exhausted, it may be extended bymanually ,adjusting the cam ring 44. Within the new range of adjustmentthus provided, the linkageI will continue to provide automaticadjustment for further facing wear.

The invention provides an arrangement which 45 i-s to be understood thatthis is by way of Villusbe in disengaged position as shown in Fig. 2,the

rotation of torque transmitting ring IIi by the power source ascontemplated will result in the free arcuate segments I1 being movedradially outwardly bringing the teeth 9a thereof into close .engagementwith the opposed teeth I2 of the vcounterclockwise direction about theirfulcrum pivots 33. The arms 31 of the levers 32 will swing tothe rightas viewed in the drawings, drawing the bolts to the right, andtransferring movement through the coil springs 49 and the washers 5I, tothe adjustment levers 40, causing the latter to swing in acounterclockwise direction. The outerarms 42 of the levers 40, bearingagainst the cam ring 44, transmit the movement to the drivenelement 20,advancing the latter to effect l clutch engagement. The reaction istransmitted from the levers 32 to the pivots 33, thence to the fulcrummember 35 and the driven element I9. Thus the two driven elements aredrawn together into clutching engagement with the drive element I3. Asengagement is attained, the spring 49 will yield, and thus the engagingpressure is fixed at `a maximum. determined by the spring tration andnot by way of limitation and the Scope of my invention isdefined solelyby the appended claims which should be construed as broadly as the priorart will permit.

I claim:

1. In a friction clutch, an annular torque- Itransmitting member havinginternal teeth, a plurality of circumferentially spaced facing carryingsegments having external teeth meshing with said internal teeth, a pairof facings secured to the respective sides of said segments, and aplurality of segments, loosely confined between said fa-cings and theends of said supporting segments and having peripheral teeth meshingwith said internal teeth and adapted to snugly engage the same under theeffect of centrifugal force, said loosely confined -segments beingadapted to be clamped between said facings during driving operationofthe clutch to minimize blacklash between said annular member and saidfacing carrying segments.

2. In a friction clutch, an annular torquetransmitting member havinginternal teeth, a plurality of circumferentially spaced facing carryingsegments having driving connection with supporting segments and havingperipheral teeth defining an annular torque transmitting ringv havingradially inwardly extending teeth on the inner periphery thereof, afirst plurality of separate circumferentially spaced segmental plateshaving radially outwardly lextending teeth on the' outer peripherythereof meshing with said inner peripheral teeth of said torque ring, apair of annular friction facings secured to the opposite sides ofeach'of said first plurality of plates and a second plurality ofcircumferentialiy spaced segmental plates interposed between the ends ofsuccessive ones of said first named plates, said second plurality ofplates having radially outwardly extending teeth and being freelymovable radially outwardly between said facings under the influence ofvcentrifugal force to effect close engagement of said teeth of saidsecond plurality of plates with the inner peripheral teeth of saidtorque transmitting ring upon said ring and Aplates being rotated priorto clutch engagement,

whereby backlash between said ring and said first plurality of segmentalplates is prevented during clutch engagement.

4. In a friction clutch arrangement, means defining an annular torquetransmitting ring having radially inwardly extending teeth on the innerperiphery thereof, a first plurality of separate circumferentiallyspaced segmental plates having radially outwardly extending teeth on theouter periphery thereof meshing with said inner peripheral teeth of saidtorque ring, a pair of annular friction-facings secured to the oppositesides of each of said first plurality of plates and a second pluralityof circumferentially spaced segmental plates interposed between the endsof successive ones of said first named plates, said second plurality lofplates having radially out.. wardly extending teeth and being freelymovable radially outwardly between said facings under the infiuence ofcentrifugal force to eect close engagement of said teeth of said secondplurality of plates with the inner peripheral teeth of said torquetransmitting ring, means including a pressure plate and means foroperating the same for engaging said friction facings therebetweensubsequent to the initial rotation of said torque ring whereby saidsecond named plurality of arcuate plates are held between said annularfacings in positions wherein the teeth thereof cooperate with the teethof said torque ring to prevent backlash between said ring and said firstsegmental plates. A

5. In a friction clutch, an annular torquetransmitting member; aplurality of circumferentially spaced facing carrying members havirgdriving connection with said torque-transmitting member; a pair offacings secured to the respective sides of said circumferentialy spacedmembers; and a plurality of centrifugally influenced members looselyconfined between said facings and the ends of said carrying members andnormally rotatable with said torque-transmitting member, and means foreffecting a snug engagement of said centrifugally influenced memberswith said torque-transmitting member under the influence of centrifugalforce for effecting a driving connection between said loose members andsaid torque-transmitting member, said loosely confined members beingadapted to be clamped between said facings during driving operation ofthe clutchwhereby to minimize backlash between said torque-,transmittingmember and said facing carrying members.

6. In a friction clutch, an annular torquetransmitting member havinginternal teeth; a plurality of clrcumferentially spaced facingsupporting members having external teeth meshing with said internalteeth to establish a driving connection with said torque-transmittingmember; friction facings secured to opposite sides of lsaid supportingmembers; a plurality of centrifugally influenced members looselyconfined bef`

